llorens



Dec. 22, 1959 L. M. LLoRENs CALCULATI'NG MACHINE KEYBOARD coN'rRoL MEANSoriginal Filed July 29. 1950 10 She'BtS-Sheet- 1 H116 11 Il ATTORNEYS.

Dec. 22, 1959 1 M. LLoRENs CALCULATING MACHINE KEYBOARD coNTRoL MEANS 10Sheets-Sheet 2 Original Filed July 29. 1950 IN VEN TOR.

TiN-4 BY ATTO R N EYS.

bec. 22, 1959 L. M. LLoRENs cALcuLATING MACHINE KEYBOARD CONTROL MEANS10 Sheets-Sheet 3 Original Filed July 29. 1950 INVENToR. v l

ATTORNEYS.

10 Sheets-Sheet 4 Dec. 22, 1959 L. M. LLoRENs CALCULATING MACHINEKEYBOARD CONTROL MEANS Original Filed July 29, 1950 JNVENToR.

ATTORNEYS.

L. M. LLoRENs cALcULATiNG MACHINE KEYBOARD CONTROL MEANS Original FiledJuly 29, 1950 Dec. 22, 1959 10 ShetS-Sheet 5 I lm,

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ATTCRNEYS.

Dec. 22, 1959 L. M. LLORENS l 2,918,217

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.INVENTORL ATTORNEYS.

Dec. 22, 1959 1 M. LLORENS 2,918,217

' CALCULATING MACHINE KEYBOARD CONTROL MEANS Original Filed July 29.1950 10 Sheets-Sheet 7 INVENTOR. ma h.

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Dec. 22, 1959 L. M. |,LoRENs CALCULATING MACHINE KEYBOARD' CONTROL MEANSOriginal Filed July 29, 1950 l0 Sheets-Sheet 8 Dec. 22, 1959 L. M.LLoRENs 2,918,217

CALCULATING MACHINE KEYBOARD CONTROL MEANS Original Filed July 29. 195010 Sheets-Sheet 9 ZEG , ATTO RNEYS.

Dec. 22, 1959 1 M` LLQRENS 2,918,217

CALCULATING MACHINE KEYBOARD CONTROL MEANS Originai Filed Jul-y 29, 1950l0 Sheets-Sheet 10 INVENTOR. Tini. ll-E. 1 L j:

ATTORNEYS.

United States Patent O 2,918,217 CALCULATING MACHINE KEYBOARD CONTROLMEANS Louis M. Llorens, Groton, N.Y.

Original application July 29, 1950, Serial No. 176,741. Divided and thisapplication November 30, 1953, Serial No. 395,050

Claims. (Cl. 23S- 130) This invention relates to calculating apparatusand more particularly to machines adapted to perform a plurality ofmathematical operations and including printing and visual totalizingmechanisms.

This application is a division of my application Ser. No. 176,741, filedJuly 29, 1950, for Calculating Machine.

One of the objects of the present invention is to pro vide novelapparatus for making mathematical computations which embodies novellyconstructed parts that are so assembled and associated in a novel mannerto perform plural functions, whereby the size, weight and total numberof parts are reduced considerably below those of known machines capableof performing comparable functions.

Another object is to provide la novel, readily-portable computingmachine which is of comparably simple construction, the parts of whichmay be assembled in an advantageous manner so as to `facilitateinspection and repair.

Still another object is to provide novel and simplified means foroperating and automatically controlling the operation of machines of theabove character whereby the possibilities of error or damage to themachine as a result of improper or injudicious operation or handling areminimized.

It is another object of ,this invention to provide a novelly constructedkeyboard unit for a calculating machine which may be novelly combinedwith the other operating parts of the structure so as to be readilyremovable without the necessity for disconnecting any operating parts oraffecting the operability of thev machine.

A still further object is to provide in apparatus of the -abovecharacter a stop-pin carriage unit of novel and simplified constructionand novel means for effecting and controlling the movements thereof.

It is also an important object of the invention to provide novellyconstructed totalizing means and novel means for operating andcontrolling the same, including novel simplified means for effecting acarry-over opera-` tion.

The above and further objects and novel features of the presentinvention will more fully appear from the following detail descriptionwhen the same is read in connection with the accompanying drawings. Itis to be expressly understood, however, that the drawings are for thepurpose of illustration only and are not intended as a definition of thelimits of the invention.

yIn the drawings, wherein like reference characters refer to like partsthroughout the several views.

Fig. l is a top plan view of a calculating machine constructed inaccordance with the present invention, the outer casing and the keyboardbeing removed and certain of the parts having portions thereof brokenaway for purposes of clearer illustration;

Fig. 2 is a vertical longitudinal or side sectional view substantiallyon the line 2 2 of Fig. 1;

Fig. 3 is a vertical longitudinal sectional view substantially on theline 3 3 of Fig. 1, with the stop-pin carriage omitted;

Fig. 4 is a fragmentary vertical transverse sectional view substantiallyon the line 4-4 of Fig. 2;

ICC

the associated totalizer actuating slide rack being broken away forpurposes of clearer illustration; t

Fig. 6 is a vertical longitudinal sectional view substantially on theline 6--6 of Fig. 1;

Figs. 7, 8 and 9 are detail side elevation views, partly in section, ofthe handle operated sector in different positions;

Fig. 10 is a fragmentary side elevation view, partly in section, showingthe totalizer and actuating mechanism therefor in position for effectinga totalizing operation;

Fig. 11 is a vertical longitudinal'sectional view, 4taken substantiallyon the line 11-11 of Fig. l; l

Fig. `l2 is a vertical longitudinal sectional viewsub-I stantially onthe line 12-12 of Fig. l;

Fig. 13 is an enlarged detail end elevation view, partly in section, ofthe stop-pin carriage; `j

Fig, 14 is a detail side elevational `view of one of the stop-pinholding springs 4shown in 4end elevatiornin Fig. 13;

Fig. 15 is a detail end elevational view, partly insee'- tion, of thestop-pin carriage escapement mechanism;

Fig. 16 is avertical longitudinal or side sectionalview substantially onthe line 16-16 of Fig; l; I

Fig. 17 is a vertical longitudinal; sectional view taken substantiallyon the line 17-17 of Fig. 1;

Fig. 18 is a detail top plan view of a portion of the totalizer unitwith the cover therefor removed forpurposes of clearer illustration;

Fig. 19 is an enlarged detail end elevational v iew, partly in section,showing a number ofthe type-quadrant locking members inassembledrelation;

Figs. 20 and 2l are enlarged top plan and side'eleva tional views,yrespectively, of-one of said type-quadrant locking members; i

Fig. 22 is a detail top plan view of the keyboard unit with the keybuttons omitted and a portion of the top plate thereof broken away forpurposes ofT clearer illustration; i

Fig. 23 is a front elevation view of said keyboard unit looking from thebottom of Fig. 22, and showing parts of the stop-pin carriage andescapement mechanism in dotted lines;

Fig. 24 is a vertical transverse sectional view on the line 24-24 ofFig. 22, and showing particularly the backspacer mechanism; t V

Fig. 25 is a side elevational view, partlyy in secton,` o' f saidkeyboard unit looking from the left -in Fig. 22, and

including the elements controlled by the non-print and subtraction keys;

Fig. 26 is a detail front elevational view, partly in section, of thesymbol selector slide of the keyboard unit, and including elementsoperated by. said slide;

Fig. 27 is a detail side elevational view, partly in section, showingthe division key depressed with associated parts;

Fig. 28 is a detail side elevational view, partly in section, showingthe subtraction key depressedwith associated parts; Y

Fig. 29 is a side elevational view, partly in section,of the keyboardlooking from the right in Fig. 22, the key lock slide being showninposition to permit depression of the total or sub-total keys; l f

Fig. 30 is a vertical longitudinal sectional view substantially on theline 30--30 of Fig. 22 showing't'he keylock slide in normal position toprevent depression of the total and sub-total keys;

Fig. 31 is a vertical longitudinal or side sectional view substantiallyon the line 31-31 of Fig. 22, the symbol Patented Dec. 22, 1959"selector slideand elements associated therewith being shown in normalpositions; v

Fig. 32 is a view similar to Fig. 31, but showing the position of theparts when printing a total;

,A Fig. 33 is a vieWksimilar to Fig. 31, but showing the position of theparts when printing a sub-total;

Fig. 34 is a detail side elevational View, partly in sectionshowing therepeat key depressed and the elements actuated thereby; l

. Fig. 35 is a detail side elevational view, partly in section, showingthe total key depressed and locked, and some of the elements actuatedthereby;

Fig. 36 is a detail side elevational view, partly in section, showingthe sub-total key depressed and locked, and some of the elementsactuated thereby;

. Fig. 37 is a detail side elevational view, partly in section, showingthe non-add key depressed and locked, and some ofthe elements actuatedthereby;

Fig. 38 is a view similar to Fig. 31, but showing the symbol-selectorlslide and associated elements in position for a non-add operation;

Fig. 39 is a detail side elevational view, partly in section, showingthe symbol controlling mechanism and the inked ribbon lifting mechanism,said mechanisms being `shown in position for elfecting a subtractionoperation;

Fig. 40 is a fragmentary side elevational view, partly in section,showing the totalizer and actuating mechanism therefor in the positionsoccupied when printing a total; n Fig. 41 is a view similar to Fig. 40,but showing the totalizer and actuating mechanism in the positionsoccupied when printing a subtotal;

Fig. 42 is a detail side elevational View, partly in section, showingparticularly the carry-over mechanism in position for effecting acarry-over;

Fig. 43 is a fragmentary front elevational view of the carry-overmechanism, viewed from the left in Fig. 42. y Fig. 44 is a fragmentaryside elevational View, partly in section, showing the totalizer andslide rack gear frame unit in raised or subtraction position;

Fig. 45 is a fragmentary vertical transverse sectional View, lookingfrom the right in Figs. 12 and 17, showing the mechanism for controllingthe raising of the rack gear frame unit of Fig. 44, the section beingtaken approximately on line 45-45 of Fig.'17;

Fig. 46 is a side elevational view of the paper and ribbon feed vunitorprinting platen assembly;

Fig. 47 is a vertical side sectional view of the unit shown in Fig. 46,the section being taken substantially on line 47-47 of Fig. 51;

Fig. 4 8 is a detail side elevational View, partly in section, of aportion of the ribbon feed mechanism;

Fig. 49 is a fragmentary front elevational view of said unit, o nareduced scale, as viewed from the left in Figs. 46 and 47; and yFigs.and 51 are complementary rear elevational views, partly in section andwith the paper supply roll removed, Fig. 50` showing elementsillustrated in Fig. 46 and Fig. 51 showing elements illustrated in Fig.47.

VINDEX TO DESCRIPTION ,4 INTRODUCTION The single embodiment of theinvention illustrated in the accompanying drawings, by way of example,is in the form of a manually-operable, readily-portable calculatingmachine of the so-called ten key type. The machine is capable ofeffecting direct mechanical addition and subtraction and may be used toreadily effect multiplication and division. Means are provided forlisting or printing the gures set into the machine as well asidentifying marks for indicating the results and the nature of thecomputations, the printing mechanism being of the socalled hammer-blowtype. The illustrated machine also embodies visual totalization oraccumulation.

In the form shown, the basic frame or support for the operating parts ofthe machine comprises a base 60 to which a plurality of uprightlongitudinally extending frame members or plates are secured in anysuitable known manner (Fig. 1). 61 and 62 serve as supports for variousoperating and stationaiy parts. Two inside frame members 63 and 64 serveas'supports and are cut away and perforated wherever necessary toaccommodate other parts. A shorter vertical frame member 66 is providedat the forward end of the machine between members 61 and 63. These tiveupright frame members are connected together by a plurality ofhorizontal tie rods or the like, most of which perform additionalfunctions and will be more specifically identied as the descriptionproceeds.

In the interest of brevity and uniformity the end of the machine nearestthe operator, i.e. the end at the bottom in Fig. 1, is herein treated asand called the front of the machine, whereas the end remote from theoperator is referred to as the rear of the machine. The terms forwardmovement and rearward movement are used to identify movements toward thefront and rear of the machine, respectively. Unless otherwise stated,the terms clockwise and counter-clockwise are used to identify movementsof pivoted parts when viewed along 4their axes from the front, top orright hand side as viewed in Fig. l, and the terms right-hand andleft-hand are used to identify movements of parts or directions asviewed from the right or the front in Fig. 1.

BASIC DRIVING on POWER INPUT MECHANISM (Figs. 1, 2, 4 and 6 m 9) Theinvention contemplates novel simplified means embodying only a smallnumber of compactly assembled parts for imparting to the operatingmechanisms the necessary power or energy and for controlling theoperating speed independently of the speed or rate at which the power isapplied. In the illustrated embodiment, operation is manually effectedby means of a handle 67 but it will be understood that electrical orother power means could be substituted. The handle is suitably andpreferably removably mounted for rotation with a rigid assemblycomprising avplate or arm 68 and a stub shaft 69 (Fig. 4) which isjournalled in a bushing in side frame member 61 and held in axiallyfixed position by a split ring engaging a groove in the shaft or byother suitable known means. Securely mounted on arm 68 and projectinginwardly through a suitable opening in side frame 61 is a pin or stud 70through which power is transmitted to the operating parts during eachforward or operating stroke of the handle, i.e. toward the operator asviewed in Figs. 1 and 4.

Rotatably journalled on shaft or rod 69 is a sieevc 77 formed integrallywith an arm or sector 71 (Fig. 2) which has a notch or groove in therear or right hand edge thereof to receive actuating pin 7G for purposesto hereinafter appear. Arm or sector 71 has an arcuate slot 72therethrough and the outer arcuate edge-surface ,thereof is smooth atthe forward end and provided with serrations or V-shaped notches 73 atthe rear end portion thereof. Said edge-surface is adapted to cooperatewith Two outside frame members a spring-'biased double acting pawl 74that is pivotally mounted on a stud projecting from the inner face offrame member 61. When the parts are in normal or non-operating position,the full stroke sector 71 and pawl 74 assume they positions shown inFig. 2, the pawl being biased counter-clockwise by spring 75. During theinitial part of the operating stroke of handle 67 when the sector 71 ismoved by pin 70 to the position shown in Fig. 7, pawl 74 rides on thesmooth edge surface of the sector so that the parts are free to returnto starting position if the handle is released. As will appearhereinafter, this feature is utilized to effect by operation of handle67 the removal of an erroneous amount which has been set in the machinethrough the keyboard or the pin carriage controlled thereby.

When, during the operating stroke of the handle, said pin 70 hasproceeded to the point represented in Fig. 8, pawl 74 will engage aserration 73 and thereafter prevent any return movement of sector 71 andother parts operated thereby until the sector passes beyond the pawl, asshown in dot and dash lines in Fig. 9. In this position the sector hasengaged a stop sleeve on a rod 76. Thus, once the pawl 74 engages ltheserrations 73, the cycle of operation thus commenced must be completed.It will be noted, however, that handle 67 and pin 70 are free for returnmovement at all times, thus eliminating any danger of introducing anerror in the calculations or causing damage to the machine by a forcedreturn stroke of the operating handle. On the return or clockwisemovement of sector 71 after each operating stroke, pawl 74 is cocked inthe opposite direction (as shown in Fig. 9) to engage serrations 73 insuch manner as to prevent any subsequent full or partial effectiveoperating or forward stroke of handle 67 or detrimental interferencewith the operating parts until the machine has completed the operatingcycle for which it has been energized by the full forward stroke ofhandle 67.

Freely journalled on the tubular hub 77 of sector 71 is a sleeve 78(Fig. 4) on which two radially extending arms 79 and 80 are rigidlysecured in axially spaced relation for angular movement therewith. Thissleeve and arm unit is connected to sector 71 through a yieldable torquetransmitting connection which, as shown, comprises a coil spring 81. Thelatter surrounds sleeve 78 between arms 79 and 80 and the opposite endsthereof engage axially extending pins or lugs 82 and 83 on arm 80 andsector 71, respectively. Extending between the outer ends of arms 79 and80 is a pin or rod 84 whereby the motion of said arms may be transmittedto other operating end control parts. The right hand headed end of rod84 extends freely through slot 72 in sector 71 and the space between thehead on rod 84 and arm 79 is sufficient to permit free relative angularmovement of said arm and sector to the extent permitted by the slot. Thereduced ends of a spacer sleeve 86 fitted between arms 79 and S0 andsurrounding rod 84 serve as bearings and provide suitable axial spacefor two links S7 and 88. Link 87 is a main operating link and has a slot89 (Fig. 2) for receiving one end of the spacer sleeve, whereas link 88is pivoted on the sleeve (Fig. 6) and constitutes part of a connectionto a speed governing mechanism to be hereinafter described.

The threaded left end of rod 84 is operably engaged by a nut 90 (Fig.4), the reduced cylindrical right hand end portion of which buttsagainst arm 80 and serves as a pivot bearing and axial spacer for a link91 (Fig. 6), hereinafter sometimes referred to as the pin carriagereturn arm. The other or left end of nut 90 is also reduced and forms anoperating pin or stud 92, the function of which in connection with thetotalizing or accumulating mechanism will be hereinafter described.

Sleeve 78 extends to the left (Fig. 4) beyond the end of shaft 69 andinto abutting engagement with a bushing or bearing inside frame member63. Passing through said bushing and into sleeve 78 and secured to thelatter by a pin or other suitable means is a stub shaft 93 to which issecured a cam 94 that performs a plurality ofA functions, as willhereinafter appear.

Certain of the above described parts may be returned to and yieldablyheld in non-operating position (Figs. 2 and 6) by a spring 96 connectedbetween a xed rod 97 or the like and a lug 98 on link 91. If desired,this spring may be connected directly to sector 71. During the initialportion of the return stroke of sector 71 from stop 76, said spring 96is assisted by other resilient means to be later described.

OPERATING-SPEED GOVERNOR (Fig. 6 and lower right hand corner of Fig. 1

Governor means of novel construction are provided in novel combinationwith the above described driving or operating means for controlling theoperating speed of the machine and for preventing too rapid operationthereof in response to direct excessive force applied by an operator orother power source. As shown, the governor mechanism (Fig. 6) is locatedin the lower right hand corner of Fig. 1 of the drawing and is connectedwith the parts which it controls through link 88 which, as mentionedabove, is pivotally connected to the movable axis 84, 86. The other endof link 88 is pivotally connected to a crank arm 99 which is in turnpivotally mounted on a rod 100 between frame plates 61 and 66 and heldin spaced relation to said plates by suitable spacer sleeves on the rod.A gear segment 101 is pivotally mounted on rod 100 and is connected tocrank 99 by a pin 102 in axially spaced relation thereto. Gear segment101 meshes with a small pinion 103 which is integrated with a largergear 104 rotatably supported on a stud 106 mounted in and projectingfrom frame plate 66. Since gear 104 is thus connected with the rockerassembly including arms 79 and 80, the speed of operation of the machineduring both the operating and return strokes of said rocker assembly maybe controlled by controlling the rotational speed of said gear.

Speed control for normal operation is obtained primarily by a simplefriction brake which, in the form shown, comprises a brake shoe orbutton 107 (Figs. 1 and 6) held in continuous yielding engagement withthe right side surface of gear 104 by a coil spring 108. Said shoe issecured to a rod 109 that is slidably received in and supported by atube 110 mounted on frame plate 61. The spring surrounds tube 110 and isinterposed under compression between brake shoe 107 and frame plate 61.The desired speed can be adjusted by varying the force or compression ofspring 108.

Centrifugally operated braking means are also provided to intermittentlycomplement the continuously operating braking means above described. Asshown, the centrifugal brake is driven by gear 104 through a pinion 111in constant mesh therewith. The latter is rotatably mounted on a stud112 secured to and projecting from frame plate 66. Integrated in anysuitable manner with pinion 111 is a plate or disc 113 to which asimilar plate 114 is secured in axially spaced relation by pins 115, 116with suitable spacing sleeves thereon between the plates. Mountedbetween plates or discs 113, 114 for rotation therewith and pivotalmovement about eccentrically mounted pins 115, are two iiyweights 117.The latter are yieldably held in normal or full line position (Fig. 6)against stops 116 by coil springs 118 interposed between laterallyprojecting lugs on disc 114 and extended portions of the weights.

A pan-shaped brake drum 119 is staked or otherwise nonrotatably securedto the end of stud 112 and the annular peripheral ange thereof surroundsthe centrifugal ily-weight assembly described above. The relationship ofthe parts is such that when Weights 117 are pivoted toward dotted lineposition (Fig. 6) against the efforts of springs 118 in response tocentrifugal force,

a knob 120 on each weight swings into frictional engagement with theinner surface of the flange of drum 119. This creates an additionalfrictional drag that limits any further increase of speed. As a furtherprecaution against any rotation of brake drum 119 the same may beconnected to frame member 61 by a pin 121 which also serves as a supportfor other parts to be described.

From the above description of the power input linkage and speed controlgovernor, it will be seen that when handle 67 and sector 71 are actuatedon a forward or operating stroke at a speed greater than that at whichcrank arms 79, 80 and hence other parts of the machine are permitted bythe governor to operate, the handle and sector may proceed in advance ofsaid arms to the extent permitted by the pin and slot connection 84, 72.This advance movement, when made necessary by the operator, merelyeffects a further tensioning of spring 81. Under proper normal operatingconditions, energy is transmitted through spring 81 so that arms 79, 80will move at the same angular speed as handle 67. Accordingly, pin 84does not normally depart appreciably from the upper or forward end ofslot 72 where it is yieldably held by the initial tension of spring 81.

. Novel means are provided for insuring a full forward or operatingstroke of the operating parts of the machine whenever there has been afull stroke of the operating handle; that is, means are provided toprevent any return movement of the operating parts independently of thereturn movement of the handle until said parts have completed a fullpower stroke. In the form shown, said means comprises a locking member122 (Fig. 2) for locking sector 71 in its forward or full strokeposition adjacent stop 76 therefor whenever the machine parts have notcompleted a full forward or operating stroke. Member 122 is pivotallymounted on rod 121 and comprises two axially spaced arms 124 and 126,the same being urged in a counter-clockwise direction by a spring 127 toyieldably maintain arm 126 against stop 76. Arm 124 is in the same planeas sector 71 and the lower rear corner thereof is squared for lockingengagement with the forward tooth or notch 73 on the sector. Extendingrearwardly and upwardly from arm 126 into the path of spacer 86 on rod84 is a finger or lug 128.

During normal or proper operation, spacer sleeve S6 engages lug 128 andpivots pawl 122 clockwise so that arm 124 will not engage a sector tooth73. However, when arms 79, 80 and, hence, sleeve 86 lag behind thesector 71 as a result of too rapid forward operation of the latter, andthe sector has passed the point beyond which locking pawl 74 is nolonger effective to prevent return movement as heretofore described,pawl arm 124 will engage a sector tooth 73 and prevent return movementof the sector. Under these conditions the sector will be released forreturn movement only after the gov n ernor has permitted spring 81 toimpart a full forward stroke to crank arms 79, 88. Release is effectedby sleeve 86 ingaging lug 128 and pivoting member 122 clockwise out oflocking engagement with sector 71, '73.

MAIN OPERATING LINKAGE (Figs. 1, 2, 3, 11, and 17) On the so-calledforward or operating stroke of handle 67, a substantial portion of theoperating parts of the machine are actuated by spring 81 which is underinitial if its ends in frame plates 61 and 63. One end of the springengages a spacer sleeve on a tie rod 131 and the other end engages a pin132 on a rocker arm 133 secured to shaft 130 for imparting oscillatorymovement thereto. The clockwise angular movement of the rocker arm bythe spring is limited by the sleeve on tie rod 131 (Fig. 2). The upperend of rocker arm 133 is pivotally secured to main operating link 87.Thus, on the counter-clockwise or operating stroke of arms 79, aftercross pin 84 engages the left or forward end (Fig. 2) of slot 89 in link87, the latter is moved to the left or forwardly, thereby rocking thearm 133 and shaft 130 counterclockwise to wind up spring 129 and toactuate and control certain of the main operating parts of the machinein a manner to be hereinafter described. It may be here noted that rod84 does not engage the forward end of slot 89 during the forward strokeof handle 67 until about the time that pawl 74 engages a serration 73 onsector 71. The prior or initial portion of said stroke is utilized topre-set some of the machine parts, such as by cam 94, in preparation foractuation or release for operation of other parts controlled by the mainoperating linkage, as will more fully appear as the descriptionproceeds.

Rigidly secured to shaft for oscillatory movement therewith is a crank134 (Fig. 3), the lower forwardly extending portion of which ispivotally connected to a link 136. The forward end of said link ispivotally secured to the lower end of the right hand end arm 137 (asviewed in Fig. l) of an oscillating arm assembly comprising dependingend arms 137, 138 rigidly connected by a cross shaft 139 journalled inframe members-63, 64. Pivotally connected to the lower ends of arms 137and 138 and extending rearwardly therefrom are two links 140 and 141,respectively. The latter are additionally connected to each other by twotransverse bars 142 and 143 which function to actuate other parts of theapparatus in a manner to be hereinafter described.

KEYBOARD UNIT (Figs. 22 to 25) Numerical data is put into the machine bymeans of digit and symbol keys mounted in a keyboard unit which isnovelly constructed and combined with the remainder of the structure insuch a manner that the same may be readily removed for purposes ofinspection and repair without in any way affecting the normaloperability of the machine. It is accordingly an easy matter to obtain afull view of the operating parts of the machine in operation to thusfacilitate discovery of the causes for operational failures. In theillustrated embodiment, the keyboard unit comprises an upper plate and alower plate 151 secured together in vertically spaced relation by fourposts 152, 153, the lower plate being removably held in place by screwswhich threadedly engage said posts. Slidably mounted in this frame areten digit keys and eight symbol or control keys, all shown in Fig. 22with the linger buttons removed in the interest of clarity.

p The digit keys are indicated by numerals 0 to 9, in-

' clusive, and the symbol or operational keys are identified as follows:non-print key 154, back spacer key 156, di- Vision key 157, subtractionkey 158, repeat key 159, total key 160, sub-total key 161 and non-addkey 162.

Each of the key members is made of a strip of metal comprising a shank163 (Fig. 23) which supports a finger button 164 and slidably extendsthrough a suitable guide slot in top plate 150. Between plates 150 and151 each key member is divided and suitably contoured to form a leg 166that slidably extends through a slot in lower plate 151 and a shorterleg 167 which is adapted to engage the lower plate to limit the downwardmovement of the key. Additionally, each of the ten digit key members hasa horizontal arm 168 which over-rides a vertically movable cross-bar 169and all except the 9 key has a pin operating leg 170 projectingdownwardly through .lower plate 151 from a horizontal arm, which in someinstances is arm 168 or an extension thereof. Aspring 171 surrounds eachguide leg 166 and yieldably supports the key in inoperative position.Although the digit key members are all differently shaped between theframe plates, each has the same basic parts and the pin operating legs170 thereof are all arranged in fore-and aft-alignment and in numericalsequence to 8) from front to back as indicated at 170, 170 (Fig. 22).The construction-of each of the symbol or control keys will be morespecifically hereinafter described when the coaction thereof with otherparts of the structure is described.

Bar 169 is supported by a bail consisting of side arms 172, 172 and across-piece 173. Said bail is pivotally mounted on reduced portions ofscrews which have threaded engagement with and project through posts 153(Fig.22) and bar 169 rests by gravity upon an upwardly biased lever 174(Figs. l5 and 23) of an escapement mechanism which controls the movementof a traveling stop-pin carriage to be next described.

TRAVELING STOP-PIN CARRIAGE (Figs. 1, 2, 13, 14, 15 and I6) Mountedbelow the keyboard for cooperation therewith and Vwith the mainoperating parts of the machine is a traveling carriage 175 which isactuated and controlled in a'novel manner and is novelly constructed tominimize the `number of parts and thereby facilitate the assembly .anddisassembly thereof. In the specific form illustrated, said carriagecomprises a frame (Fig. 13) consisting of a top plate 176 and a bottomplate 177 secured together and vertically spaced by side plates 178,178. The forward ends of the latter are slotted and the rear endsthereof are perforated to receive tie rods 179 and 180, respectively,which extend between outside frame members 61 and 62 and support thecarriage for reciprocating movement transversely of the machine belowthe keyboard.

The upper and lower plates of the stop-pin carriage frame havevertically aligned slots therein, arranged in transverse rows andlongitudinal columns, there being nine pairs of vertically aligned slotsin each row and column in the illustrated structure. Slidably mountedand guided in each said pair of vertically aligned slots is astop pin181. Each pin has two Vshaped notches in the right hand edge thereof, asviewed in Fig. 13, and oppositely facing shoulders on the left edge thatengage plates 176 and 177 to. limit the vertical movement of the 1n. pEach pinlSI is yieldably held in one of its two limiting positions bynovel resilient means. For each longitudinal column or row of pins 181there is provided a single comb-like resilient member 182 (Fig. 14) thatts between adjacent longitudinal columns or rows of the pins-and betweenright hand side plate 178 and the first row of pins on the right. Eachresilient comb member 182 consists of a series of nine resilient tongsor fingers 183 with V-shaped end portions that normally engage the lowergrooves or notches in the pins 181 and a solid portion A184 thatyieldably engages the flat surfaces of the pins in the adjacentlongitudinal row. Each resilient comb 182 may be readily removed bysliding it endwise from the carriage frame so that worn or defectivesprings may be readily replaced. The pins 181 in the front transverserow or line are adapted to be engaged and moved downwardly by the 0 keymember to a position such that a spring finger 183 engages the uppernotch in the pin and the lower end of the pin extends below lower plate177 (dotted position 181:1, Fig. 13). The pins in thenext or secondtransverse row toward the rear are similarly operable by the 1 key, thenext or third row by the 2 key and so on, the last or rear row beingoperable by the 8 key. Return or upward movement of a stop-pin 181 iseffected by a cam surface 186 ina manner to be hereinafter described.

The stop-pin carriage is normally biased for movement toward the leftside of the machine, as viewed in Fig. 1, by a spring 187 anchored toframe plate 62 (Fig. l) and upper plate 176 adjacent the right hand edgethereof (Fig. 13). Movement of the carriage by the spring is controlledby an escapement mechanism comprising arm 174 pivotally mounted on abracket projecting from frame plate 64 (Figs. 1 and 15) and biased in acounterclockwise direction by a spring 188, as viewed from the front ofthe machine. The free end of arm 174 extends into a guide slot in frameplate 63 which limits the upward or counter-clockwise movement thereof.Pivotally mounted on arm 174 is a pawl 189, the free end of which isbiased upwardly by a spring 191) to a limiting position determined by alug 191 on arm 174i. Said lug projects lforwardly from arm 174 to theimmediate left of the nose of pawl 189 for engagement thereby and thelug and pawl cooperate with a slotted member or rack 192 secured tohorizontal ears on the rear edge portions of the carriage side plates178 to control the step-by-step movement of the carriage toward theleft, as viewed from the front. The teeth or prongs 193 of rack 192project rearwardly from the carriage and corresponding surfaces thereof'are transversely spaced to correspond with the transverse spacing ofthe longitudinal or fore-and-aft columns or rows of stop-pins 181. Whenescapement arm 174 is in normally raised position, the nose of pawl 189extends into a notch between the teeth of the rack 192 and preventsmovement of the carriage toward the left by spring 187. Whenever arm174l is depressed by bar 169, which is in turn depressible by each digitkey as heretofore described, the nose of the escapement pawl 189 willmove below the rack 192, 193. Simultaneously, lug 191 will move into thenotch vacated by the pawl, thus permitting the carriage to move slightlyto the left into engagement with said lug. When arm 174 is now pivotedupwardly by spring 188 upon release of the digit key and bar 169, thecarriage is released by lug 191 moving out of the rack notch, butmovement of the carriage is shortly stopped again by pawl 189 whichenters the next rack slot to the right under the tension of spring 190.Thus, as the digit keys and, hence, bar 169 are successively depressedand released, the carriage will be moved with a step-by-step movement tothe left by spring 187 under the control of the escapement mechanism.The longitudinal or fore-and-aft columns of pins 181 are thussuccessively moved into vertical alignment with the row of stop-pinactuating legs on the digit key members.

The lower ends of stop-pins 1.81 which have been depressed serve asstops for denominational slide racks to be hereinafter described. Aspointed out above, the "9 key does not operate any stop pins, but ratheronly the bail bar 169 to effect a step movement of the stop-pin carriage175. For stopping said slide racks in the 9 position, the rear edge ofbottom plate 177 on the carriage has a depending stop flange 194.

Return or right hand movement of the stop-pin carriage and tensioning ofspring 187 is effected through the medium of a bell crank, an arm 196 ofwhich is bifurcated or forked and straddles an upward extension of oneof the screws whereby rack 192 is secured to the carriage (Fig. l). Saidbell crank is pivotally mounted on a horizontal bracket projecting fromframe member 63 and the other arm 197 thereof extends toward the rightfrom the pivot for engagement by the operating link 91 which, when movedrearwardly during the return stroke of handle 67 and sector 71 willactuate the crank to impart left-to-right movement to the stop-pincarriage as viewed in Fig. 1. During this return movement, the lowerends of any stop-pins 181 which have been depressed will operativelyengage and be moved to normal or up-position by the inclined surface 186on a laterally projecting lip 11 198 which is formed integrally withinside frame member 63 and functions as a cam. The left face of the noseof escapement pawl 109 is also tapered or inclined so that the teeth ofrack 192 will be effective to depress the pawl against the efforts ofspring 190 during the return movement of the carriage and rack.

As above pointed out, link 91 is effective to actuate crank 196, 197 toreturn carriage 175 to the right, and for this purpose said link has anupper arm 144 with. a right angle lug 145 which is engageable with thefor-- ward edge of crank arm 197. The rear or right hand end4 of pivotedlink 91 is biased upwardly or counter-clockwise by spring 96 to normallyhold the upper edge of a lower arm 146 of the link in engagement with asleeve on tie rod 131 (Fig. 6). The forward end portion 147 of said.upper edge of arm 146 is tapered or curved forwardly' and upwardly tofunction as a cam surface. Thus, when. link 91 approaches the end of itsrearward stroke and'. after the carriage 175 has been fully returned,surface 147 engages the sleeve or tie rod 131 and cams link 91 clockwisesufficiently to move upper arm 144, 145 down-- wardly out of engagementwith carriage return crank arm 197. In this manner, link 91, 144 is sopositioned as to not interfere with subsequent left hand movement of thepin carriage.

CORRECTION OF ERROR (Figs. l, 2, 6, 7 and .13)

Any suitable means may be provided for actuating lever 196, 197 orcarriage 175 independently of the rest. of the machine for removing fromthe carriage any data which has been erroneously set therein bydepression of the wrong digit keys. In the illustrated embodiment, themechanism above described is novelly constructed so that such an errormay be corrected by clearing the pin carriage through a partial strokeof handle 67. For this purpose, advantage is taken of the initialmovement of operating handle 67 which is permitted by slot 89 in link 87before the main operating linkage is brought into operation and beforepawl 74 operatively engages a serraton 73.

During the aforesaid initial movement of handle 67, the pin carriagereturn link or arm 91 is moved forwardly to the dotted line positionillustrated in Fig. 6. In this. position, the upper arm 144, 145 of link91 will have been lifted by spring 96 into the same horizontal planewith crank arm 197. Now, if handle 67 is retutrned or permitted toreturn to its normal position by the operator or by spring 96 undercontrol of the governor, link 91, 145 will engage crank arm 197 andfunction in the manner above described to return carriage 175 to itsrightmost position. During this movement, all depressed pins 181 will belifted to normal position as they pass over cam 186. The proper forwardposition to which handle 67 should be moved will be easily recognizableby the operator because the initial movement is against the relativelylight spring 96 whereas the required energy is greatly increased fortensioning main spring 129 when pin 84 engages the end of slot 09.

When only one or more of the last digits set in the machine areerroneous, it may sometimes be convenient to remove the same withoutcompletely clearing the pin carriage in the manner just described. Thismay be accomplished by use of the back spacer key 156 as willhereinafter appear. f

DENOMINATEONAL SLIDE RACK ASSEMBLIES (Figs. I, 5, 16 and 42) The figuresand symbols entered in the machine through the medium of the keyboardand the stop-pin carriage are mechanically translated into thetotalizing and printing mechanisms in a novel manner through a novelarrangement and assembly of slide racks and associated controlstherefor. In the illustrated machine, there are nine identicaldenominational slide racks, each of which is fabricated from a pluralityof parts including a printing rack member or slide 200 and a totalizerrack member or slide 201. The latter is supported in vertical or 0nedgeposition and guided for straight line longitudinal movement by upper andlower circumferentially grooved rods 202 and 76, respectively, and oneof a series of spool-like bushings 206 on the rod 131 that passesthrough a central elongated cut-out or slot 203 in rack member 201. Thelatter engages the reduced portion 204 between the anges of the bushing206 mounted on rod 131. The flanges of adjacent bushings 206 are spacedby a reduced hub portion 205 on one end of each bushing for a purpose toappear hereafter (Fig. 42). The forward end of rack slide 201 isbifurcated and the inner or adjacent surfaces of the furcations 207 and208 are provided with gear teeth for a purpose which will appearhereinafter in connection with the description of the totalizingmechanism.

On the left side (Fig. 1) of each totalizer slide 201, a printing slide200 is mounted for longitudinal movement therewith and limited movementrelative thereto. The mounting or connection of the pairs of slides 200and 201 is effected by two shouldered studs 209, the reduced portions orShanks of which are secured to slide 200 and ride in grooves 210 in rackmember or slide 201. A tensioned spring 211 is connected at its left end(Figs. 16 and 42) to a downwardly extending lug 212 on slide 200 and atits other end to slide 201 thereby exerting a force which tends to movethe slides relative to each other to cause pins 209 to occupy the righthand ends of slots 210, as seen in Fig. 42. The upper Surface of slide200 is formed with a ledge or shoulder 213 for cooperation withstop-pins 181, a series of notches 214, in the central portion forcooperation with a locking member 216, and a series of gear teeth 217for cooperation with a printing type quadrant 218 or 250, all in themanner and for purposes which will hereinafter appear. The upper surfaceof slide 201 has a shoulder 219 for cooperation with a detent 222 all inthe manner and for purposes which will hereinafter appear.

As pointed out above, slide 200 is biased toward the right (Fig. 42)relative to slide 201 by spring 211 and both slides are additionallybiased and movable toward the right by a spring 223 connected between adepending lug 224 on slide 200 and a xed horizontal tie rod 226 mountedin the frame. Return or forward movement of the slide racks 200, 201toward the left and tensioning of springs 223 is effected by main spring129 acting through a linkage comprising horizontal cross bar 142 thatextends through slots 203 and engages the rear vertical edges of thedepending portions 227 of slides 200. AS pointed out above, bar 142 issupported at its ends by a pair of identical links 140, 141 (Figs. 11and 17) the rear or right hand ends of which are supported and connectedby rod 143 that travels in and is guided by slots 228, 229 in the insideframe members 63 and 64, respectively. The forward or left end-s oflinks 140, 141 are pivotally connected to the lower ends of the sidearms 137, 138 of the oscillating arm assembly which includes horizontalrock shaft 139. The lower end of arm 137 is also pivotally connected tolink 136 which is in turn pivotally connected to rocker arm 134 whichoscillates with rock shaft 130 and, hence, with the double rocker arm133 to which spring 129 is connected. Suitable slots or openings 230 areprovided in frame members 63 and 64 to permit fore-and-aft movement ofrack operating rod 142.

lt will thus be seen that when main operating link 87 is moved forwardlyand shaft 130 is rocked counterclockwise (Figs. 2 and 3) during theforward or operating stroke of handle 67, the lower end of rocker arm134 will move rearwardly and, hence, transmit rearward movement to bar142 through link 136, arm 137, rock shaft 139, arm 138, and links 140,141. This rearward movement of slide rack operating bar 142 releasesrack assemblies 20'0, 201 for rearward movement under the influence ofsprings 223 and performs additional functions in connection with thecontrol and actuation of other units of the machine as will hereinafterappear. The extent of the rearward movement of each rack 200, 201 uponrelease thereof by rod 142 is determined in a manner to appear hereafterin accordance with the figure or amount which has been set in themachine through the keyboard. Briey, the rearward movement of the slideracks is determined by the position of stop-pin carriage 175y and anydepressed stop-pins 181 which are engageable by shoulders 213 on rackmembers 200. When the forward stroke of handle 67 is completed and theparts are' released by pawls 74 and 124 for the return stroke ormovement, spring 129 becomes effective through the abovedinkage toreturn the rod 142 and, hence, slide racks 20'0, 201 to normal position(Fig. 16) and to thereby l'again tension springs 223.

SLIDE RACK MOVEMENT CONTROL (Figs. 1, 4, l2 and 6 Before slide racks200, 201 are released for rearward movement by movement of rackoperating rod 142 to the rear on the operating stroke of the handle,suitable locking means are put in operation to prevent rearward movementof the slide racks in columns in which no digit has been set through thekeyboard and stop-pin carriage. For simplifying the description andfacilitating an understanding of the construction, let us assume thatonly the digit 5 has been set into the machine by depressing the 5 digitkey. As previously explained, depression and release of the 5 key willmove a stop-pin 181 to its lower or depressed position as indicated at181a (Figs. 13 and 16). This will be the sixth stop-pin toward the rearin the first or left column of pins on the pin carriage 175. Uponoperation of the digit key, the escapement mechanism functions to permitthe carriage to move one step to the left (Fig. l) so that the depressedpin 181:1 is moved into alignment with the first or right handdenominational slide rack 200 and in the path of shoulder 213 thereof.

Now, upon the subsequent initial forward movement of operating handle 67and before operating rod 142 begins to move rearwardly, cam 94 (Figs. 4and l2) rotates counter-clockwise with sleeve 78 and permits a link 231normally supported by the cam to move downwardly under the influence ofa spring 232 (Fig. 17). Link 231 is'guided at its lower end by a headedstud 233 engaging a slot therein and is pivotally connected at its upperend by means of a pin 234 to a bail which consists of a transversecross-bar 237 and rearwardly extending end ears 238 which pivotallysupport said bail on a shaft or tierod 239. The spring 232 is connectedunder tension between bar 237 and an upwardly biased element 240 to belater described.

Resting on bail bar 237 are a series of locking pawls 220'(Fig. 16), onefor each slide rack. Said pawls are pivotally mounted on shaft 239 andeach is individually biased in a counter-clockwise direction by a bentspring 241 coiled around shaft 239 and having one end thereof secured tothe pawl and the other end in operative engagement with the rock shaft139. A forwardly extending arm ot' the pawl has a laterally off-setdepending portion 242 adapted to move into the pathof shoulder 219 ofthe slide rack 201 and prevent rearward movement of said rack. The endof arm 242 is preferably guided in the rack guide slots in rod 202. Adownwardly and rearwardly extending arm 243 of each pawl 220 is adaptedto engage the lower plate 177 of stop-pin carriage 175 when the latterhas moved to the left into the path of said'pawl arm. The pawls 220, 243which thus engage the pin carriage are prevented from pivotingcounterclockwise into rack locking position, i.e. with arm 242 in thepath of shoulder 219 when bail bar 237 is lowered.

It will thus be seen that when cam 94 is rotated to permit link 231 andbail 237 to move to down position (dotted line, Fig. 16), those pawls220, 243 which are not held orstopped by the pin carriage plate 177 willbe moved by springs 241 to rack locking position. Accordingly, under theconditions assumed above, the locking pawl 220 for the right hand digitrack 200, 201 will engage the carriage and leave said rack free to moverearwardly until the shoulder 213 thereof engages the depressed stop pin18161 (dotted lines, Fig. 16). All the other pawls 220, 242 will pivotcounter-clockwise into position to be engaged by shoulders 219 and thuslock the remainder of the slide racks 201 in normal position so the samecannot move rearwardly even when released by operating rod 142. Near theend of each cycle of operation, after rod 142 and racks 200, 201 havebeen returned to their forward positions, cam 94 is effective t0 liftarm 231, bail 237 and, hence, all ofthe rack locking pawls 220, 242 tonon-locking position (full lines, Fig. 16) in readiness for the nextcycle of operation and to permit movement of the stop-pin carriage tothe left.

PRINTING MECHANISM (Figs. I, 5, 11, 16, 17, 19, 20 and 21) The inventioncomprehends a novelly constructed simplied mechanism which functions ina novel manner with a minimum number of parts to effect so-calledhammerblow printing of the figures and symbols entered in the machine.1n the form illustrated, said printing mechanism comprises ten numeraltype quadrants 218 and a symbol type quadrant 250, each individuallymounted for oscillation on a bodily movable pivot 251. An arcuateportion or segment of each quadrant 218 concentric with said pivot isprovided with gear teeth 252 in constant mesh with the teeth 217 on arack slide 200 (Fig. 16). To each quadrant 218 there is secured anarcuate type bar or strip 253 each bearing in sequence, from top tobottom, the numerals 0 to 9, inclusive. On quadrant 250 the type bar orstrip has various symbols designed to assist the operator ininterperting the printed figures. In all other respects quadrant 250 isidentical with and functions in the same manner as quadrants 2.18.

The pivot 251 for each type quadrant 218 is mounted on and carried bythe upwardly extending arm of a bellcank member 254 journalled forpivotal movement on the reduced hub portion 205 of one of the spools orbushings 206 on lixed rod 131. Each said crank 254 is biased for pivotalmovement in a clockwise direction (Fig. 16) by a spring 256 anchored toa stationary rod 257 or a pin 258. Means in the form of a rake or comb259 are provided for holding crank members 254 against clockwisemovement by springs 256 until the type quadrants 218 have been pivotedcounter-clockwise (Fig. 16) about pivots 251 to desired pre-printingpositions determined by the rearward movements of the racks 200 in meshtherewith. Said comb 259 extends transversely across the machine betweenthe frame members 63, 64 and is pivotally mounted at its ends on a fixedrod 260 mounted in said frame members. Said rod has axiallyspaced,circumferential grooves 262 in which the upper forward ends of cranks254 are guided. The rear edge of comb 259 is slotted to form a series ofteeth 261, the ends of which are bent downwardly to hook over the upperrear edges of cranks 254 and thereby releasably lock the latter innormal position (full lines, Fig. 16).

The means for actuating comb 259 to release cranks 254 comprises a bellcrank pawl 263 (Fig. 17) pivotally mounted on a rod 264 and having arearwardly extending arm with a laterally extending lug 266 adapted toengage a downwardly facing ledge 267 on a link 268. The latter ispivotally mounted on comb 259 eccentrically with respect to pivot 260and is biased in a clockwise direction by a spring 269 to therebyyieldably hold link 268 in engagement with lug 266 on pawl 263 andyieldably hold comb 259 in locking position. Pawl 263 has aforwardly-extending arm 270 engageable by rack operating rod'142 duringthe forward movement of the latter and a downwardly extending arm 271engageable by rod 142 during the latter portion of the rearward movementthereof in the manner heretofore described. Thus, when rod 142 is movedto the rear, it engages arm 271 and imparts counter-clockwise movementto pawl 263. The lug 266 on the pawl engages ledge 267 and lifts link268, thereby pivoting comb 259 to non-locking position (dotted lineposition in Fig. 16) and releasing all the type quadrant supportingcranks 254. Each type quadrant which has been moved to a pre-printingposition, such as dotted line position A, by a rack slide 200 inaccordance with data entered into the machine, will now be carried by acrank 254 under the influence of a spring 256 into printing position B.Suicient clearance is provided between the meshing teeth on the rackslides 200 and quadrant gear segments 252 to compensate for the smallarcuate movement of pivots 251. The desired numeral or symbol on a strip253 is thus snapped into engagement with an inked ribbon overlying apaper strip on a suitable platen 272 to be hereinafter described.

Those type quadrants which have not been moved to a pre-printingposition by rearward movement of their cooperating slide racks 200 areheld against rearward movement toward the platen in a novel manner byother locking means controlled by said rack slides 201. As shown, saidother locking means comprises the series of overlapping hook members ofdetents 222 which are pivotally mounted on the transverse stationary bar264 and may depend upon gravity for their operation in a clockwisedirection toward operative locking position (Fig. 16). Each hook member222 comprises laterally spaced rearwardly extending arms 273 and 274(Figs. 19 to 21). Arm 273 is in the form of a downwardly facing hookwhich rides on and operatively engages a pin 276 secured to andextending laterally to the left (Fig. l) from a crank 254 to hold thelatter and, hence, the type quadrant 218 mounted thereon againstmovement to printing position B by a spring 256 when comb 259 is movedto unlocking position to otherwise release cranks 254. A cam lug 277extends downwardly from arm 273 into cam groove 221 in the upper surfaceor rack slide 201 so that, when said slide moves rearwardly with itsassociated slide 200 to actuate a type quadrant 218 into a pre-printingposition A, cam lug 277 will ride out of notch 221 onto the upper edgeof slide 201 and thereby lift hooked arm 273 out of the path of pin 276.The crank 254 on which said pin is mounted will then be free to move thetype quadrant 218 thereon from preprinting position A to printingposition B upon release of said crank by locking comb 259. Part of theupper edge portion 278 of each rack slide 201 is offset toward the rightto provide a better track for detent lug 277.

The novel construction of the present machine is such that upon theinitial rearward movement of bar 142 during each cycle of operation,each rack slide 200 is moved rearwardly by springs 211 and 223 through adistance determined by the pin and slot connections 209, 210 to therebymove each type quadrant to "0 pre-printing position, independently ofwhether or not its cornpanion slide 201 is locked against rearwardmovement by a pawl 220, 242. For each column in which the operator hasnot set a numeral larger than 0, there will be no further rearwardmovement of either slide of the denominational rack assembly 200, 201and the slide 201 thereof will not therefore be effective to lift thedetent or hook member 222 associated therewith to non-locking position.Th detents 222 are accordingly novelly constructed and interlocked insuch a manner that all said detents to the right (Fig. 1) of the detentin the left-most column in which the operator has set a numeral or digitgreater than "0 will be moved to non-locking position, thereby freeingthe corresponding cranks 254 and the quadrants 218 thereon for movementto printing position. Thus, in each column to the right of the left-mostdigit wherein a digit greater than 0 has not been set, the machine willprint a 0. To accomplish this result, the right-hand arm 274 of eachlocking hook or detent 222 has a laterally offset end portion 279 whichextends to the right beneath and engages the lower surface of theleft-hand arm 273 on an adjacent detent 222. Thus, when one detent islifted to non-locking or inoperative position by rearward movement of aslide 201, all said detents to the right thereof (Fig. l) will also becorrespondingly lifted to non-locking position independently of anyrearward movement of the slides 201 associated therewith. In columns tothe left of the left-most digit set in the machine, the detents 222 willremain in locking position and thus hold the corresponding typequadrants against movement to printing position.

The type quadrant operating cranks 254 are returned to normal positionby the forward movement of main operating bar 142. For this purpose eachcrank 254 has a forwardly extending arm 280 with an inclined or camsurface 281 which moves upwardly into the return path of bar 142 whenthe crank members pivot clockwise to printing position. Thus, when theoperating bar 142 is moved forwardly, it first disengagcs arm 271 oflocking pawl 263 thereby freeing link 268 and comb 259 for movement tonormal or locking position by spring 269. The force of the latter isalso exerted through shoulder 267 and lug 266 to pivot pawl 263clockwise (Fig. 17). Further clockwise movement of said pawl 263 isthereafter effected by engagement of bar 142 with the lower edge of arm270 on the pawl. Following the release of pawl 263, bar 142 engages camsurfaces 281 on crank arms 280 and pivots cranks 254 in acounter-clockwise direction (Fig. 16) a sufiicient amount to permitlocking comb 259 to be snapped into locking position by spring 269.

In order to guard against possible movement of rack slides 200 while thetype quadrants are in printing position against the platen 272 and toinsure accurate horizontal alignment of the numerals printed by the typequadrants when in printing position, means are provided for locking andaligning said racks during movement of the type quadrants into printingposition. As shown herein, said means comprises the locking comb 216made up of a transverse cross-bar with spaced forwardly and downwardlyprojecting teeth 282 and end arms 283 and 284 (Figs. 5, ll and 17). Thelatter are pivotally mounted on frame plates 63 and 64, respectively, bymeans of eccentric screws 286 for purposes of adjustment and are biasedclockwise to non-locking position by two springs 287. Each of the arms283 and 284 extends downwardly and forwardly from its pivot andterminates in an inclined surface 288 in the path of rack operating bar142. Near the end of its rearward stroke prior to its engagement withpawl arm 271 to release the type quadrants for movement to printingposition. bar 142 rides up on the forward ends of arms 283 and 284 andpivots the same counter-clockwise. This brings aligned teeth 282 intofirm engagement and mesh with notches 214 on the slide racks 200 toproperly align the said racks and positively hold the same againstmovement during actuation of the type quadrants 218.

TOTALIZER MECHANISM (Figs. 1, 3, 10, 12, I6, I8 and 40 I0 44)Totalization of the numerical data set into the machine through thekeyboard unit is effected by novel means combined and novelly cooperablewith slide rack assemblies 200, 201. As shown, the forward end of eachslide rack 201 is forked or bifurcated and the furcations 207 and '208thereof have gear teeth on the inner or adjacent surfaces thereof foralternate cooperation with pinions or gears 290 (Figs. 16 and 42). Forcomputations in addition, which will be first considered, pinions orgears 290 engage the lower toothed arms on furcatQIlS. ,207, Each of theten slide rack gears 290 is rigidly epinal? 'integrated with a totalizerdrive gear 291 and a bushing 292 which is journalled on a shaft 293 andfunctions also as an axial spacer fer adjacent gear assemblies 290, 291.Shaft or rod 293 is supported at its ends in the side wall plates 294and 295 of a vertically movable frame which includes a tie plate 296connecting 'the bottom edges of said side plates. The latter haveoppositely disposed slots in the upper and lower edges thereof near therear edges which receive horizontal tie rods 202 and 76, respectively,which extend between frame plates 63 and 64. Said gear assembly frame isthus guided by said rods for limited straight line vertical movement topermit the gear assemblies 290, 291 to be bodily lifted sufficiently sothat pinions 290 will disengage toothed arms 207 and engage toothed arms208 when direct subtraction is to be effected. Thus, when the arm 207 ofa slide rack 201 is in mesh with a pinion 290 and said rack movesrearwardly a distance determined by the magnitude of a digit set intothe machine, the gear assembly 290, 291 associated therewith will turncounter-clockwise a proportional amount and upon the return or forwardmovement of the rack 201, the gear assembly will rotate an equaldistance in a clockwise direction.

Such return or clockwise movements of gears 290, 291 during successivecycles of operation are effectively accumulated and a summation thereofand, hence, a summation of the numerals set into the machine is visiblyindicated in a totalizer unit 297. The latter comprises a rigid frame298 which is pivoted on a shaft or rod 299 that is supported by andmovable with the slide lrack gear assembly frame 294, 295. Mounted inframe 298 for individual rotation on a shaft 300 are ten number wheelassemblies 301 each consisting of a number wheel 302 bearing numerals to9, a gear 303 having ten teeth adapted to mesh with driving gear 291,and a radially projecting carry-over release pin 304, the purpose ofwhich will be later described (Figs. 16 and 18). When totalizer frame298 is in normal or raised position (Fig. 16), the number wheelassemblies 301 are held against rotation by a locking comb 306 pivotallymounted on said frame and having spaced teeth or fingers 307 which arebent downwardly at their ends for engagement with adjacent teeth ongears 303. Comb 306 is normally resiliently biased counter-clockwise tolocking position by a spring 308. A cover plate 309 is provided with atransverse slot or window 310 through which an operator can view onlyone numeral on each wheel 302.

The accumulator or totalizer carriage 297 is normally supported in up orinoperative position by a pair of cam hook lift arms 311, 312 carried byand rotatable with a rock shaft 313 journalled in the side plates 294,295 of the slide rack gear frame. Cam surfaces on arms 311, 312 engage atie rod 314 in the totalizer frame 297 and control the pivotal movementof the latter, said surfaces being so shaped as to permit said frame tolpivot clockwise and move number wheel gears 303 into mesh with drivinggears 291 when said arms are pivoted clockwise from the normal positionshown in Figs. 12 and 16. Said arms hook over rod 314 and positively'hold the totalizer unit 297 in operative position (Fig. l0) with saidrod resting on tabs 316 formed on thef gear frame side plates 294 and295. Tabs 316 are madesufficiently thin, vertically, to be adjustablefor varying:

-to the left' from' the upper end of a double rocker arm.

18 319 (Fig. l0) journalled on a stud 320 mounted on and extending tothe right from inner frame plate 63. Rocker arm 3119 preferablycomprises two spaced plates (Fig. 1) between which two oppositely facinghooks or pawls 321, 322 are guided. The upper hook or pawl 321 isadapted to engage a spacer on pin 318-between said plates and hook 322is adapted to engage a similar spacer on a pin 323 connecting the lowerends of said plates.

Pawls or hook 321, 322 are pivoted on and movable with a totalizer shiftarm 324 and the rear ends of said pawls are connected by a spring 326 tothereby bias the hooked ends thereof in outward or diverging directions.Shift arm or slide 324 is supported on-edge for limited straight linehorizontal movement by shouldered screw 327 and sleeve 78 which engageslots 315 and 325, respectively, in the slide. Forward or left handmovement of slide arm 324 is effected through a pin 328 which cooperateswith a pawl 329. Said pin is carried by the lower end of arm 137 whichis actuated in a manner heretofore described and pawl 329 is pivotallymounted on slide 324 at 330 near the rear end thereof. Said pawl has aylower finger 331 that engages bottom frame member 60 to limitcounter-clockwise movement thereof, a middle finger 332 with a forwardlyinclined lower face riding on sleeve 78 to effect clockwise movement ofthe pawl when arm 324 moves forwardly, and a top downwardly-hookedfinger 333 which cooperates directly with pin 328 in a manner to be nextdescribed.

On the forward or operating stroke of the handle 67, pin 328 is carriedrearwardly with arm 137 from normal inoperative position (Fig. 3) asheretofore described. The pin engages the tapered forward end (loweredge) of pawl finger`333, lifts it and proceeds past the rearwardlyfacing hook thereon. The pawl finger 333 then drops again by gravity toits stop or normal position determined by arm 331. At the beginning ofthe return stroke, as distinguished from the operating stroke, pin 328moves to the left engaging the hooked upper finger 333 of pawl 329 tothereby impart forward movement to said pawl, shift arm 324 and pawls321, 322 until pawl 329 is shifted clockwise out of hooked engagementwith pin 328 by the coaction of the tapered middle pawl finger 332 withthe upper surface of sleeve 78.

During this limited forward movement of slide arm 324 when the parts areset for addition or accumulation, pawl 321 is in operative engagementwith pin 318 on the upper end of rocker arm 319. Pawl 322 is at thistime supported out of engagement with pin 323 by a pin 334 projectinglaterally to the left from a rocker lever 336 to be later described.Accordingly, forward movement Iof pawl 321 with arm 324 causescounter-clockwise movement of said rocker arm 319 and, hence, forwardmovement of pin 318 which actuates arms 317, 311 clockwise to movetotalizer unit 297 to its lowered or operative position (Fig. 10) in themanner previously described. As said unit is lowered, a projection 337on locking comb 306 engages frame plate 294 and pivots the combclockwise, thereby lifting the fingers 307 thereof out of lockingengagement with the number wheel gears 303. After unit 297 has thus beenlowered, the slide racks 201 are returned by bar 142 to normal forwardor starting position, thereby rotating gear assemblies 290, 291 andnumber wheel assemblies 301. The gear ratios are such that the rotationof the number wheels in each column will be proportional to the size ormagnitude of the number set in the machine in that column.

The totalizer unit 297 is again lifted out of operative engagement withgears 291 near the end of the return stroke of each operating cycle. Atthis time, pin 92 whichl projects to the left from operating armassembly 79, engages the front edge of an upwardly projecting lug 338 atthe rear end of shift arm 324 and moves the latter rearwardly. Thismovement of shift arm 324 is translated intocounter-clockwise pivotalmovement 0f 19 totalizer unit 297 through pawl 321, pin 318, arm 317,arms 311, 312 and tie rod 314.

A booster detent 339 cooperates with rocker assembly 318, 319 toyieldably maintain the totalizer frame in its limiting positions. Saiddetent is pivotally mounted on frame plate 63 and has a V-shaped bottomedge surface at the free end thereof which is biased by a spring 340into continuous engagement with a roller 341 on the pin 318 (Figs. 3 and10). When the unit 297 is in its limiting positions, one side or theother of said V- shaped surface engages said roller and exerts ayielding effort in the proper direction to hold the frame in thatposition. Detent 339 also functions to snap the frame into its limitingpositions after the roller 341 passes beneath the point or crest of saidV-shaped surface on the detent.

CARRY-OVER MECHANISM (Figs. I, I2, 16, 17, 42 and 43) Whenever one ofthe number wheels 302 has made a complete revolution from a position inwhich is visible in window 310, it becomess necessary to carry anadditional digit over into the next adjacent column to the left. Forexample, when the numeral 9 on the right hand wheel 302 has reachedwindow 310 and one is added thereto, the summation is 10, thus making itnecessary to move the second (from the right) number wheel to l or tothe next higher number for which it is then set. This result is obtainedin the illustrated machine by novel means constituted by a very smallnumber of simply constructed parts in comparison to prior known meansfor accomplishing the same purpose.

In the form illustrated, said carry-over mechanism comprises a series ofspring biased carry-over pawls 342 pivotally mounted on a tie-rod'343 onthe inner frame plates 63 and 64. Each said pawl is formed from a thinpiece of sheet metal bent to channel shape for bearing purposes and hasat its left end (Fig. 43) two angularly disposed arms 344 and 345 in thesame plane (Fig. 42). The ends of arms 345 are bent to the left at rightangles to form tabs 346 which function as stops, when in normalposition, for limiting the normal forward movement of slide racks 201.Each pawl 342 is normally biased in a counter-clockwise direction by aspring 347.

Arms 344 of pawls 342 cooperate with a series of locking members 348which are pivotally mounted on a tie-rod 349 between frame plates 63, 64and have downwardly and rearwardly extending notched arms 350 engaged bypawl arms 344 when in normal position (Fig. 16). In the samelongitud'nal plane with notched arm 350, each locking member 348 has anupwardly extending arm 351 on which is mounted a pin 352 that extendslaterally to the right (Fig. 43) into the slot of a downwardly extendingforked arm 353 of a carryover release pawl 354. There is a correspondingseries of said release pawls pivotally mounted on a tie-rod 356 betweengear frame plates 294, 295. Each release pawl 354 is biasedcountercloekwise by a sprng 357 and has a second arm 358 extendingforwardly between adjacent gear assemblies 290, 291 in the same plane asthe inner end of forked arm 353 of the same pawl. Release pawl arms 358terminate with inverted V-shaped humps 359 on the upper surfaces thereofimmediately below number wheels 302 for cooperation with the radiallyextending pins 304 on the number wheels. Each said pin is locatedbetween the numerals 5 and 6 on the number wheel so that as the wheelmoves counter-clockwise from "9 to 0 in window 310, pin 304 will engagehump 359 and cam the release pawl 354 in a clockwise direction (Fig. 42)against the efforts of a spring 357. Forked arm 353 of said pawl is thusswung to thel left (Fig. 42) and pivots pawl lock 348 counter-clockwiseto release stop pawl 342. The latter, when thus released, pivotscounterclockwise under spring tension and frees the slide rack 201 whichoperates the adjacent number wheel to the left for additional forwardmovement. This additional forward movement of the rack is effected byspring 211 and the extent thereof, determined by the length of slots 210in the slide rack 201, is just sufficient to rotate the proper numberwheel one tooth or one-tenth of a revolution and thus bring up the nexthigher number thereon in the window 310.

A pin 304 depresses and passes over a hump 359 in the same cycle ofoperation, so that any release pawl 354 and associated member 348 arereturned immediately to normal position by a spring 357. Stop pawls 342which have beenv released are reset to normal position during theoperating stroke of the next cycle of operation after the slide racks201 controlled thereby have been moved rearwardly by springs 223 intoengagement with either pawls 220, 242 or a stop-pin 181 on the stop-pincarriage 175. The illustrated means for effecting the resetting of pawls342 comprises a bail 359 consisting of a cross-bar 360 and two bellcrank end arms 361, 362 (Figs. l2 and 17) pivotally mounted on the endsof the tie-rod 343 outside the gear frame side plates 294, 295.Cross-bar 360 is engageable with pawl arms 345 and the upper ends ofarms 361, 362 are pivotally connected to the links 363 of identicalsplit or longitudinally extensible links 363, 364 at opposte sides ofgear assembly 294, 295. Link 364 carries headed pins which slide inslots 366 of link 363 and the two links 363, 364 are yieldably held innon-extended or shortened relation by a spring 367 and link 364 isbiased forwardly by a spring 368. The rear end of link 364 is guided andsupported by a stud 369 that engages a slot 370 in the link. Downwardlyprojecting lugs 371 at the rear ends of links 364, are in the path ofrack operating bar 142 so as to be engageable thereby during the lastpart of the rearward movement thereof. Rearward movement of links 363,364 in this manner pivots crank arms 361, 362 in a clockwise direction,thereby lifting bail bar 360 in a clockwise arc to reset stop pawls 342to the position illustrated in Fig. 16 in readiness to stop the racks201 on the return or forward movement thereof unless said pawls aretripped again for the purpose of effecting a carry-over in the mannerdescribed.

PRINTING A TOTAL (Figs. I, 2, 3, 1], 12, I6, 22, 29, 30, 35 and 40) Thetotal or summation of the numbers put into the machine is continuouslyvisually indicated by number wheels 302 through window 310. Novellyconstructed and novelly operable means are provided for printing thistotal at the will of the operator and for simultaneously removing thesummation from the number Wheels in readiness for another computation.In the specific form shown, said means is under the control of a totalkey which is normally locked against depression by a laterally extendinglug 376 thereon that overlies a flat upper surface on key lock slide bar377 (Fig. 30). The latter is guided and limited in its fore-and-aftmovements by stationary pins 378 that are threaded into posts 152 in thekeyboard frame and extend through slots in the slide bar. A spring 379anchored on a pin 378 and connected to a pin 380 on the rear end of theslide bar 377 normally holds the latter in its foremost position (Fig.30). Means to be next described are adapted to move the slide barrearwardly to its mid-position (Fig. 29), and positively hold it againstforward movement. In this mid-position, lug 376 of the total keyoverlies the inclined upper surface of a locking tooth 381 on the slidebar. Thus, when the key is depressed, the slide bar is cammed rearwardlyuntil lug 376 passes tooth 381, whereupon spring 379 snaps the bar 377forwardly to cause tooth 381 to overlie lug 376 and lock the total keyin depressed position (Fig. 35).

Movement of key lock slide bar 377 to therear is

